JP2007211934A - Cage for radial needle bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To realize a structure in which appropriate regulation of the amount of lubricating oil accumulated in each needle installing part and the amount of lubricating oil that passes through are made easy, in a structure for regulating the radial position of a cage 7a by guiding of an outer diameter side raceway. <P>SOLUTION: Through-holes 16, 16 are provided to parts of rim parts 11, 11 constituting the cage 7a. Alternatively, recessed grooves with both ends communicating with outside surfaces of the rim parts 11, 11 and the inside of pockets 13, 13 are formed on the outer peripheral surface at an end of the cage 7a. The problem is solved by this structure which enables the lubricating oil in each of the pockets 13, 13 to be appropriately discharged. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an improvement of a cage incorporated in a radial needle bearing that constitutes a rotation support portion of an automobile transmission or various mechanical devices. Specifically, it is intended to realize a structure capable of rotating at high speed and ensuring excellent lubrication performance.

  A radial needle bearing is incorporated in a portion to which a large radial load is applied in a rotation support portion of an automobile transmission or various mechanical devices. For example, a planetary gear type transmission that constitutes an automatic transmission of an automobile supports a planetary gear rotatably with respect to a carrier by a radial needle bearing as described in Patent Document 1 and the like. 8 to 9 show an example of a planetary gear type transmission that has been widely known in the past. This conventionally known planetary gear type transmission includes a sun gear 20 having teeth 20a formed on the outer peripheral surface, and a ring gear 21 disposed concentrically with the sun gear 20 and having teeth 21a formed on the inner peripheral surface. A plurality (generally 3 to 4) of planetary gears 4 and 4 are arranged at regular intervals in the circumferential direction. The teeth 4a formed on the outer peripheral surfaces of the plurality of planetary gears 4 and 4 are meshed with the teeth 20a and 21a. Further, as shown in FIG. 9, in order to rotatably support the planetary gears 4 and 4, the support gears are supported at a plurality of locations in the circumferential direction of a pair of support plates 2a and 2b which are parallel to each other. Both ends of the shaft 3 are supported and fixed. The planetary gears 4 are rotatably supported by radial needle bearings 5 around the intermediate portion of the support shaft 3. During the operation of the planetary gear type transmission, the planetary gears 4 and 4 revolve around the sun gear 20 at high speed while rotating around the support shaft 3 at high speed.

  The radial needle bearing 5 holds a plurality of needles 6 and 6 by a cage 7 so that the needles 6 and 6 can roll freely. The outer peripheral surface of the intermediate portion of the support shaft 3 is a cylindrical inner ring raceway 8. The inner peripheral surface of each of the needles 6 and 6 is in rolling contact with the inner ring track 8 and the outer ring track 9. Further, floating washers 10a and 10b are disposed between the both axial end surfaces of the planetary gear 4 and the inner side surfaces of the two support plates 2a and 2b, respectively. The frictional force acting between the inner surfaces of the support plates 2a and 2b is reduced.

  The cage 7 constituting the radial needle bearing 5 is arranged in an axial direction (left and right direction in FIGS. 10 to 11) with a space between each other, as shown in detail in FIGS. A pair of rim portions 11, 11 and a plurality of column portions 12, 12. These column parts 12 and 12 are intermittently arranged in the circumferential direction, and both end parts thereof are made to be continuous with the outer diameter portions of the inner side surfaces of the rim parts 11 and 11 facing each other. . Moreover, each said pillar part 12 and 12 has the shape where the axial direction intermediate part bent in the trapezoid shape toward radial inside. Then, the pockets 13, 13 are defined as space portions surrounded by four sides by the circumferential side opposite edges of the column parts 12, 12 adjacent to each other in the circumferential direction and the mutually opposite inner side surfaces of the rim parts 11, 11. The needles 6 and 6 are held in the pockets 13 and 13 so as to roll freely.

  The retainer 7 protrudes in the circumferential direction from the side surfaces thereof, with the locking projections 14 and 14 being aligned with each other in the circumferential direction of both side surfaces of the pillars 12 and 12. It is provided in the state to do. These locking projections 14 and 14 prevent the needles 6 and 6 that are held in the pockets 13 and 13 so as to roll freely from coming out of the pockets 13 and 13 radially outward. belongs to. That is, when assembling the needles 6 and 6 together with the cage 7 between the inner ring raceway 8 and the outer ring raceway 9 (see FIG. 9), the needles 6 and 6 are placed in the pockets 13 and 13, respectively. It is necessary to hold in a state in which it is prevented from coming out in the radial direction.

For this purpose, the locking projections 14 and 14 are provided on the outer diameter side of the pitch circle of the needles 6 and 6 at the openings of the pockets 13 and 13 so as to face each other. The distance D ₁₄ (see FIG. 10) between the leading edges of the locking projections 14 and 14 is made smaller than the outer diameter D ₆ (see FIG. 9) of the needles 6 and 6 (D ₆ > D). ₁₄ ). At the same time, the distance D between the opposite side edges of the inner diameter side locking portions 15, 15 located at the inner diameter side of the pitch circle of the needles 6, 6 at the intermediate portion of the pillar portions 12, 12. ₁₅ (see FIG. 10) also outside is smaller than the diameter _{D 6 (D 6> D 15} ) of the needles 6.

In order to hold the needles 6 and 6 in the pockets 13 and 13, the needles 6 and 6 are pushed into the pockets 13 and 13 from the inner diameter side of the cage 7. At this time, the distances D ₁₅ between the side edges of the inner diameter side locking portions 15 and ₁₅ are elastically widened by the needles 6 and 6, and the needles 6 and 6 are passed between the side edges. . In the state where the needles 6 and 6 are held in the pockets 13 and 13 in this way, the needles 6 and 6 are respectively connected to the outer sides of the cage 7 by the locking projections 14 and 14. In addition, the side edges of the inner diameter side locking portions 15 and 15 of the column portions 12 and 12 are prevented from coming out in the same radial inward direction. Although not shown, each needle may be incorporated into each pocket from the outer diameter side of the cage. There is also a cage that does not have the locking protrusions 14 and 14 and the inner diameter locking portions 15 and 15.

  During the operation of the radial needle bearing incorporating the cage 7 as described above, the installation portions of the needles 6 and 6 (the rolling surfaces of the needles 6 and 6, the inner ring raceway 8 and the outer ring raceway 9 are It is necessary to feed a sufficient amount of lubricating oil to the rolling contact part). In particular, in the case of the radial needle bearing for supporting the planetary gear, since the needles 6 and 6 revolve while rotating at high speed, the lubrication condition becomes severe, and the effect of feeding the lubricating oil to the installation portion is effective. Must be done manually. Usually, the lubricating oil that passes through the inside of the radial needle bearing and is discharged to the outside is used for lubricating peripheral members installed around the radial needle bearing. For this reason, the radial needle bearing needs to have a structure that can ensure the amount of lubricating oil that circulates without interfering with the passage of the lubricating oil. In view of such circumstances, Patent Document 2 employs an inner diameter side raceway guide structure that restricts the radial position of the cage by bringing the inner circumferential surface of the cage and the inner ring raceway close to each other. A structure is described in which the thickness of the gap between the outer peripheral surface of the cage and the outer ring raceway is secured to secure the amount of lubricating oil flowing through the installation portion.

However, in the case of such a structure described in Patent Document 2, contact between the inner peripheral surface of the cage and the outer peripheral surface (inner ring raceway) of the support shaft is a problem due to the action of centrifugal force acting during operation. There is a possibility. That is, as described above, the planetary gear revolves at a high speed while rotating at a high speed when the automatic transmission for automobiles provided with the planetary gear is operated. As a result, a large centrifugal force acts on the lubricating oil present on the inner diameter side of the planetary gear, and this lubricating oil tends to concentrate on the radially outer side (upper side in FIG. 9) of the carrier 1. Furthermore, a large centrifugal force also acts on the retainer during operation of the automobile automatic transmission. For this reason, in the case of the structure described in Patent Document 2 that employs the inner diameter side raceway guide, as shown exaggeratedly in FIG. 12A, the inner peripheral surface of the cage 7 and the support shaft 3 May contact the outer circumferential surface of the carrier 1 at the radially inner side of the carrier 1 where the lubricating oil tends to be insufficient {lower side in FIG. 9, X portion in FIG. 12A), and wear may occur at the contact portion. is there. Such a problem becomes a problem when the rotation speed of the planetary gear exceeds 10,000 min ⁻¹ , especially when the rotation speed exceeds 20,000 min ⁻¹ .

  In Patent Document 3, the radial dimension of the gap between the outer peripheral surface of the cage and the inner peripheral surface of the outer ring raceway is regulated to a range of 2.5 to 4% of the outer diameter of the cage. A structure for securing the amount of lubricating oil existing (retaining) in the installation part is described. However, when the invention described in Patent Document 3 is used for a radial needle bearing for supporting a planetary gear, the following problems may occur. That is, as exaggeratedly shown in FIG. 12B, the outer peripheral surface of the retainer 7 and the outer ring raceway 9 which is the inner peripheral surface of the planetary gear 4 are caused by the centrifugal force acting on the retainer 7 during operation. There is a possibility that the amount of lubricating oil that contacts with the outer side in the radial direction of the carrier 1 (upper side in FIG. 9, Y part in FIG. 12B) and passes through the installation part is reduced. For this reason, in the case of the invention described in Patent Document 3, it is difficult to properly regulate the amount of the lubricating oil passing through the installation portion, and the cooling effect by the lubricating oil becomes insufficient, and the radial needle There is a possibility that the peripheral members installed around the bearing cannot be sufficiently lubricated.

  When the amount of the lubricating oil staying is small, the lubrication of each rolling contact portion becomes poor, and when the amount of the lubricating oil passing through is small, the temperature rise of each rolling contact portion cannot be suppressed, and the radial needle The peripheral members installed around the bearing cannot be sufficiently lubricated. Ensuring the amount of lubricating oil staying in the installation portion is mutually contradictory to ensuring the amount of lubricating oil passing therethrough. In the case of the invention described in Patent Document 3, a relatively large gap exists between the outer peripheral surface of the cage and the outer ring raceway depending on the outer diameter of the cage. There is a possibility that the radial position of the cage cannot be sufficiently regulated and the cage vibrates during high-speed operation. In consideration of these matters, in order to sufficiently ensure the reliability and durability of the radial needle bearing, the radial position of the cage is set so that the outer circumferential surface of the cage and the outer ring raceway are closely opposed to each other. It is desired to realize a structure that can be controlled by the side raceway guide and that can easily regulate the amounts of both types.

JP 2002-235841 A JP 11-336770 A JP-A-2005-180501

  In view of the circumstances as described above, the present invention has a structure in which the radial position of the cage is designed by an outer diameter side race ring guide in which the outer circumferential surface of the cage and the outer ring raceway are closely opposed to each other, and each needle The present invention has been invented to realize a structure in which the amount of lubricating oil staying in the installation portion and the amount of lubricating oil passing therethrough can be appropriately regulated.

Each of the radial needle bearing retainers according to the present invention has a pair of rim portions that are arranged concentrically with an interval in the axial direction and each has an annular shape, and spans between the two rim portions. A plurality of pillar portions. The portions surrounded by the four rims by both the rim portions and the column portions adjacent to each other in the circumferential direction serve as pockets for holding the needles in a freely rollable manner. Further, the positioning in the radial direction is used in a state where the outer peripheral surface and the outer ring raceway are closely opposed to each other by the outer diameter side race ring guide.
In particular, in the radial needle bearing retainer according to claim 1, a penetration that communicates the outer side surface and the inner side surface of the rim portion with a part of at least one of the rim portions. A hole is provided.
In the radial needle bearing retainer according to claim 2, at least one of the outer peripheral surfaces in the axial direction at one end outer peripheral surface, one end at the outer surface of the rim portion, and the other end at the end Recessed grooves are formed directly inside the pocket or through spaces existing around the pillars.

According to the radial needle bearing retainer of the present invention as described above, the structure in which the radial position of the retainer is achieved by the outer diameter side raceway guide that causes the outer peripheral surface of the retainer and the outer ring raceway to closely face each other, In addition, it is possible to realize a structure in which the amount of lubricating oil staying at each needle installation portion and the amount of lubricating oil passing therethrough can be easily regulated appropriately.
That is, in the state where the lubricating oil is concentrated radially outward based on the centrifugal force during high speed operation, the amount of the lubricating oil staying at each needle installation portion and the amount of the lubricating oil passing therethrough are the same as those of the rim portion. Changing the cross-sectional area of the through-hole formed in part (in the case of the invention described in claim 1) or the concave groove formed in the outer peripheral surface of the end of the cage (in the case of the invention described in claim 2) It is adjustable. Adjustment of the two kinds of amounts based on the cross-sectional area of such a through hole or a concave groove is easy, and can be performed regardless of the distance between the outer peripheral surface of the cage and the outer ring raceway (the width of the annular gap).
For this reason, the radial position of the cage can be properly regulated by the outer diameter side raceway guide, and the two kinds of amounts can be appropriately adjusted. In addition, a sufficient amount of lubricating oil can be supplied to peripheral members installed around the radial needle bearing. In the case of the present invention, in order to achieve the radial position of the cage by the outer diameter side raceway guide, the contact between the cage and the support shaft is made as in the structure described in Patent Document 2 described above. There is no problem.

[First example of embodiment]
1 and 2 show a first example of an embodiment of the present invention corresponding to claim 1. The feature of this example is based on the premise of the structure used by the outer-diameter-side track ring guide that positions the outer peripheral surface and the outer ring raceway 9 in close proximity to each other, as shown in FIG. The amount of lubricating oil staying in the pockets 13 and 13 for holding the needles 6 and 6 (see FIG. 9) to be freely rotatable inside each of them and the amount of lubricating oil passing through the needles 6 and 6 appropriately This is to realize a structure that is easy to regulate. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 8 to 11 described above, the overlapping description will be omitted or simplified, and the following description will focus on the characteristic parts of the present invention.

  The retainer 7a of this example is a saddle-shaped retainer formed by pressing a metal plate such as a steel plate or a stainless steel plate as in the case of the conventional structure described in FIGS. In the case of this example, a part of the pair of rim parts 11, 11 constituting such a cage 7 a and a part in which the phase in the circumferential direction coincides with each of the pillar parts 12, 12 respectively. Through holes 16 and 16 are formed to communicate the outer side surface and the inner side surface of the rim parts 11 and 11.

  Such a cage 7a holds the needles 6 and 6 in the pockets 13 and 13 to form a radial needle bearing, and rotatably supports the planetary gear 4 (see FIG. 9) around the support shaft 3. . In this state, the outer peripheral surface of both axial ends of the cage 7a and the outer ring raceway 9, which is the inner circumferential surface of the planetary gear 4, are closely opposed over the entire circumference, and the positioning of the cage 7a in the radial direction is performed. Is achieved by engagement with the outer ring raceway 9. During operation, from the lubricating oil supply path (not shown) having the downstream end opened to the outer peripheral surface of the support shaft 3, on the inner diameter side of the retainer 7 a, between the pair of rim portions 11, 11, Discharge the lubricating oil. This lubricating oil collects on the inner peripheral surface of the planetary gear 4 based on the centrifugal force accompanying the rotation of the planetary gear 4 and also causes the revolutionary motion of the planetary gear 4 (rotational motion of the carrier 1 shown in FIG. 9). Based on the accompanying centrifugal force, the carriers 1 gather outside in the radial direction.

  In the case of this example, both end portions in the axial direction of the cage 7a (the outer peripheral edges of the pair of rim portions 11, 11) are close to and opposed to the outer ring raceway 9 over the entire circumference. The amount of lubricating oil discharged from between the outer peripheral edge of the portions 11 and 11 and the outer ring raceway 9 is limited. Further, since each of the through holes 16 and 16 is formed in a portion closer to the inner diameter than the outer peripheral edge of the rim portions 11 and 11 (the radial intermediate portion of the rim portions 11 and 11), Even if the lubricating oil is discharged from the holes 16, 16, the lubricating oil remains in the outer portions of the through holes 16, 16 with respect to the radial direction of the cage 7 a. The lubricating oil remaining in this portion adheres to the rolling surfaces of the needles 6, 6, and the inner ring raceways of the rolling surfaces of the needles 6, 6, the outer ring raceway 9, and the outer peripheral surface of the support shaft 3. 8 is used for lubrication of the rolling contact portion. Therefore, a sufficient amount of lubricating oil can be supplied to these rolling contact portions even during high-speed operation.

  Further, the lubricating oil in the space where the needles 6 and 6 are installed is discharged to the outside through the through holes 16 and 16 and is always replaced with the lubricating oil supplied from the lubricating oil supply path. The amount of lubricating oil that moves to the outside in the radial direction of the carrier 1 based on the centrifugal force accompanying the revolving motion and is not discharged through the through holes 16 and 16 is sufficient for lubrication of the rolling contact portions. And is gradually discharged from the outer ring raceway 9 and the outer peripheral edges of both the rim portions 11, 11. Therefore, the temperature rise of the lubricating oil existing in the space is limited. For this reason, the radial needle bearing 5 (see FIG. 9) can be effectively cooled by the lubricating oil. A sufficient amount of lubricating oil can also be supplied to peripheral members (not shown) installed around the radial needle bearing 5. Further, unlike the structure described in Patent Document 2, the contact between the cage 7a and the support shaft 3 does not become a problem. As a result, the reliability and durability of the radial needle bearing 5 can be improved.

  In the above example, the case where the respective through holes 16 and 16 are formed in both the rim portions 11 and 11 has been described. In this case, it is preferable that the downstream end of the lubricating oil supply passage is opened at the center position of both the rim portions 11 and 11 from the viewpoint of evenly distributing the lubricating oil in the space. On the other hand, each of the through holes 16 can be formed only in one rim portion 11. In this case, the downstream end of the lubricating oil supply path is opened at a position close to the other rim portion 11 among the positions between the pair of rim portions 11 and 11. Then, the lubricating oil discharged from the downstream end of the lubricating oil supply path flows from the other rim portion 11 toward the one rim portion 11.

[Second Example of Embodiment]
FIG. 3 shows a second example of an embodiment of the present invention corresponding to claim 1. In the case of this example, an inclined portion inclined toward the center side in the width direction of the retainer 7b with respect to the portion near the outer diameter of the rim portion 11a at the end of the retainer 7b with respect to the portion closer to the inner diameter of the rim portion 11a. 17 is formed. The inclined portion 17 is formed with a through hole 16a that allows the outer surface and the inner surface of the rim portion 11a to communicate with each other. In such a structure of this example, the formation position of the through hole 16a exists in a portion near the outer diameter of the cage 7b. By appropriately regulating the area of the through hole 16a, each needle The amount of lubricating oil staying in the installation portion and the amount of lubricating oil passing therethrough can be appropriately regulated. The configuration and operation of the other parts are the same as in the case of the first example of the embodiment described above.

[Third example of embodiment]
4 to 5 show a third example of the embodiment corresponding to the second aspect. Also in this example, as shown in FIG. 9 described above, the feature is the structure used by the outer diameter side raceway guide that aims at positioning in the radial direction by making the outer peripheral surface and the outer ring raceway 9 face each other. As a premise, the amount of lubricating oil staying in the pockets 13 and 13 for holding the needles 6 and 6 (see FIG. 9) to be able to roll on the inner side, and the amount of lubricating oil passing therethrough, It is in the point of realizing a structure that is easy to regulate properly. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 8 to 11 described above, the overlapping description will be omitted or simplified, and the following description will focus on the characteristic parts of the present invention.

  The retainer 7c of this example is a saddle-shaped retainer formed by pressing a metal plate such as a steel plate or a stainless steel plate as in the case of the conventional structure described in FIGS. In the case of this example, the concave grooves 18 are respectively formed on the outer peripheral surfaces of both ends of the cage 7c in such a manner that the outer peripheral edges of the pair of rim portions 11 and 11 reach the both end portions of the column portions 12 and 12, respectively. , 18 are formed. Each of the column portions 12 and 12 is present at both end portions near the outer diameter portion of the cage 7c and at the center portion near the inner diameter portion, and these both portions are continued by the inclined step portions 19 and 19, respectively. ing. Both end portions of the concave grooves 18 and 18 open to the outer side surfaces of the rim portions 11 and 11 and the inner side surfaces of the inclined step portions 19 and 19 (surfaces on the center side in the width direction of the cage 7c), respectively. ing.

  Such a cage 7c also constitutes a radial needle bearing as in the case of the first example of the above-described embodiment, and the planetary gear 4 is rotatably supported around the support shaft 3 and the cage 7c. Is positioned by engagement with the outer ring raceway 9 (see FIG. 9). Further, during operation, a portion between the pair of rim portions 11, 11 is formed on the inner diameter side of the retainer 7 c from a lubricating oil supply path (not shown) having a downstream end opened on the outer peripheral surface of the support shaft 3. Then, the lubricating oil is discharged. The behavior of this lubricating oil is also the same as in the first example of the above embodiment.

  In the case of this example, the concave grooves 18 and 18 are present on the outer peripheral surface of the retainer 7c. By appropriately regulating the cross-sectional area of the concave grooves 18 and 18, each needle installation portion It is possible to appropriately regulate the amount of lubricating oil staying in the cylinder and the amount of lubricating oil passing therethrough. The configuration and operation of the other parts are the same as in the case of the first example of the embodiment described above. In addition, since each said recessed groove 18 and 18 is the part which aligns with each said column part 12 and 12, and is formed in the part where the intensity | strength and rigidity of both said rim parts 11 and 11 are high, each said each As the concave grooves 18 and 18 are formed, the strength and rigidity of the rim portions 11 and 11 are not lowered so as to be a substantial problem.

[Fourth Example of Embodiment]
6 to 7 show a fourth example of the embodiment of the invention corresponding to claim 2. In the case of this example, the grooves 18a and 18b are respectively formed in the outer peripheral surfaces of the pair of rim portions 11 and 11 constituting the cage 7d at the portions where the phases in the circumferential direction match the pockets 13 and 13, respectively. , And in a direction inclined with respect to the central axis of the cage 7d. Each of the concave grooves 18a and 18b is formed as a pair by combining the concave grooves 18a and 18b having different inclination directions at both ends of the pockets 13 and 13, respectively.

  In the case of such a structure of this example, the lubricating oil present in each of the pockets 13 and 13 with the rotation of the retainer 7d causes the rim portions in the concave grooves 18a and 18b. 11 and 11 are discharged out of the pockets 13 and 13 through the recessed grooves 18a (18b) inclined in the direction toward the rear in the rotational direction as they go toward the outer side surfaces. For this reason, the groove 18a (18b) forcibly discharges the lubricating oil in the pockets 13 and 13 to cause a kind of pump action, thereby reducing the cross-sectional area of the grooves 18a and 18b. However, a sufficient amount of lubricating oil can be distributed. For this reason, in the case of this example, even if the concave grooves 18a and 18b are formed in portions of the rim portions 11 and 11 that are aligned with the pockets 13 and 13, the rim portions 11, 11 strength can be secured. The configuration and operation of the other parts are the same as in the case of the third example of the embodiment described above.

In each case of the above-described embodiment, the cage is made of metal. This is based on the premise that the radial needle bearing retainer of the present invention is used under conditions where the rotational speed of use exceeds 10,000 min ^-1 , and in particular, when it is severe, it exceeds 20,000 min ^-1. This is because metal is advantageous in terms of securing the strength. However, the present invention can be used in a cage made of synthetic resin under conditions where the rotational speed of use is not so high. Furthermore, if the present invention is applied to a cage made of a high-functional resin having high strength, it can be used for applications where the rotational speed of use is high. In any case, in the case of a cage made of synthetic resin, it is easier to process than a metal cage, and the manufacturing cost can be reduced.

The perspective view of the 1st example of an embodiment of the invention. FIG. The figure equivalent to the AA expanded sectional view of FIG. 2 which shows the 2nd example of embodiment of this invention. The perspective view which shows the 3rd example. The side view similarly seen from the outer diameter side. The perspective view of the 4th example of an embodiment of the invention. The side view similarly seen from the outer diameter side. The schematic side view which shows an example of the planetary gear type transmission conventionally known. CC sectional drawing of FIG. The perspective view which similarly shows one example of the retainer for radial needle bearings. BB sectional drawing of FIG. Sectional drawing of the rotation support part of the planetary gear located in the upper left part of FIG. 8 shown in order to demonstrate the disadvantage of a prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Carrier 2a, 2b Support plate 3 Support shaft 4 Planetary gear 4a Tooth 5 Radial needle bearing 6 Needle 7, 7a, 7b, 7c, 7d Cage 8 Inner ring track 9 Outer ring track 10a, 10b Floating washer 11, 11a Rim part 12 Column Part 13 Pocket 14 Locking protrusion 15 Inner diameter side locking part 16, 16a Through hole 17 Inclined part 18, 18a, 18b Groove 19 Inclined step part 20 Sun gear 20a Teeth 21 Ring gear 21a Teeth

Claims (2)

  A pair of rim portions arranged in a concentric manner with an interval in the axial direction, each having an annular shape, and a plurality of pillar portions spanned between the two rim portions, The part surrounded by the rim part and the column part adjacent in the circumferential direction is used as a pocket to hold the needle so that it can roll freely, and the positioning in the radial direction is close to the outer peripheral surface and the outer ring raceway. In a radial needle bearing retainer used in a state where the outer diameter side race ring guides the outer rim, the outer side surface and the inner side surface of the rim portion are formed on a part of at least one of the rim portions. A radial needle bearing retainer, characterized in that a through hole is provided to communicate with the radial needle bearing.   A pair of rim portions that are concentrically arranged at intervals in the axial direction, each having an annular shape, and a plurality of column portions that are spanned between the two rim portions; The part surrounded by the rim part and the column part adjacent in the circumferential direction is used as a pocket to hold the needle so that it can roll freely, and the positioning in the radial direction is close to the outer peripheral surface and the outer ring raceway. In the radial needle bearing retainer used in a state where the outer diameter side raceway guide is intended to be used, the outer peripheral surface of at least one of the outer peripheral surfaces in the axial direction is disposed on the outer peripheral surface of the rim portion. The radial needle bearing retainer is characterized in that a concave groove is formed through the other end directly inside the pocket or through a space existing around the pillar portion.

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